Motor-grader implements

ABSTRACT

Apparatus for earth-working which consists of motor-grader mobile apparatus of the type which carries a subframe element in adjustable planar relationship with respect to the earth, said subframe providing adjustable support for a cutting and trimming implement which includes a first earth-cutting and moving implement in coactive combination with a moldboard for adjustable positioning and contact in a pre-set plane of said earth&#39;&#39;s surface.

United States Patent [191 Swisher, Jr. et a1. May 29, 1973 541MOTOR-GRADER IMPLEMENTS 3,610,341 10/1971 Swisher et a1. .,172 4.53,423,859 1/1969 Swisher et al. ..37/l08 [75] f f P" Dmlw 2,068,4331/1937 Peterson 172/7s5x 5mm, SPWeY, all 0 3,490,539 1/1970Hilmesetal.... ..37/10s x 1 Oklahoma Y Okla- 3,568,778 3 1971 SwisheretaL. ..172/785 1 2,379,469 7/1945 Bagan 172/119 X 3 Asslsnw 8 Oklamma3,091,373 6/1963 West ..172 119x k 3,136,078 6/1964 Renault 172/7s4x 22Filed: Oct 19 1970 3,503,450 3/1970 Day ..172/119 X [21] PP 1 3 PrimaryExaminer-Robert E. Pulfrey Assistant Examiner-R. T. Rader RelatedApphcat'on Data Attorney-Dunlap, Laney, Hessin & Daugherty [63]Continuation-impart of Ser. No. 793,274, Jan. 23,

l 1969, Pat. No. 3,568,778. [57] ABSTRACT 52] U 8 Cl 172/785 172/71172/119 Apparatus for earth-working which consists of motor- [511 1:3023/12 grader mobile apparatus of the type which carries a [58] Fi d 781 3subframe element in adjustable planar relationship 1727785 z' 'g ia {22with respect to the earth, said subframe providing ad- 3 6 5 9 justablesupport for a cutting and trimming implement which includes a firstearth-cutting and moving imple- 56 R f d ment in coactive combinationwith a moldboard for. 1 e e adjustable positioning and contact in apre-set plane of UNITED STATES PATENTS Said earths Surface- 2,494,3241/1950 Wright I. ..172/793 11 Claims, 16 Drawing Figures SHEET 6 OF 9PATENTEU HAY 2 91975 MOTOR-GRADER IMPLEMENTS CROSS-REFERENCE TOCO-PENDING APPLICATIONS The subject matter of the present inventionconstitutes a continuation-impart of U.S. Patent application Ser No.793,274 now U.S. Pat/No. 3,568,778 entitled Improvements in Motor-GraderApparatus," as filed BACKGROUND OF THE INVENTION 1. Field of theInvention The invention relates generally to mobile earth- .workingmachinery and, more particularly, but not by way of limitation, itrelates to improvements in earth-- working implements asadjustablycarried by motorgrader superstructure.

2. Description of the Prior Art The prior art includes various types-ofgrading machinery utilizing differing forms of articulation and drivesystems. Most prior art teachings have been directed toward improvementsrelating to the classic type of motor-grader which consistsof such as ascraper blade carried on a movable ring assembly beneath mobilesuperstructure, which blade assembly serves in an earth-cutting andearth-displacing capacity, such blade being adjustable as to lateralangle, forward angle, pitch, etc. Some prior designs of gradermachineryhave been directed to double articulated machinery similar insome respects to that which is fully disclosed in the above-citedco-pending patent applications, and

these are exemplified by a prior art U.S. patent to Wright, U.S. Pat.No. 2,494,324. This patent, as well as many other patents of relatedteaching adhere to the more classic form of grader machinery and merelyemploy the cutting and displacing blade for performing the standardgrading operation.

SUMMARY OF THE .INVENTION The present invention contemplates ,adoublearticulated motor-grader assembly which carries a compoundearth-working implement-which is adjustably controlled to carry outcutting, trimming and spreading'opcrations as a unitary operation. In amore limited aspect, the invention consists of motorfgrader structureincluding mobile ground support elements and an adjustable central framewhich carries a further adjustable subframe in controllable positionwith relation to a selected ground plane. The subframe assembly thencarries an earth-working implement consisting of a rotary cutter elementand a moldboard or scraper element arranged generally parallel thereto,both elemerits operating in co-action to function in contact at theselected earth plane.

Therefore, it is an object of the present invention to provideamotor-grader assembly for performing more efficient cutting andearth-displacing operations along a longitudinal alignment axis.

It is also an object of the invention to provide motorgraderapparatushaving increased power and traction capabilities which enable the use ofthe compound earth-working implements of increased size with appreciableprecision and ease of handling.

It is still further an object of the present invention .to provide amotor-grader assembly carrying a rotary cutting element and moldboardelement which can be controlled from a selected external referencesource to perform automated profile grade-cutting.

Finally, it is an object of the present invention to provide anattachable earth-working implement for carriage by a motor-graderassembly, which implement is capable of carrying out plural, compoundworking earth-working functions in concert.

Other objects and advantages of the invention will be evident from thefollowing detailed description when read in conjunction with theaccompanying drawings which illustrate the invention.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a side elevation of amotor-grader assembly constructed in accordance with the invention;

FIG. 2 is a top plan view of the motor-grader assembly as shown in FIG.I;

FIG. 3 is an enlarged elevation with parts shown in cutaway of a mobileassembly as constructed in accordance with the invention;

FIG. 4 is an enlarged top plan view of a mobile assembly of theinvention with parts shown in cutaway;

FIG. 5 is a section taken along linesS-S of FIG. 1;

,FIG. 6 is an enlarged section as taken along lines 6-6 of FIG. 5;

FIG. 7 is an enlarged side elevation of the main frame of the inventionwith parts shown in cutaway;

FIG. 8 is a front elevation of one form of anger assembly as utilized inthe invention;

FIG. 9 is a front elevation of a portion of an alternative form of augerassembly, a cutter-auger element, as utilized in the present invention;

FIG. 10 is a schematic diagram of the main frame tilt control assembly;

FIG. 11 is a schematic diagram of the subframe cros slope controlassembly;

. FIG. 12 is a schematic diagram of the steering control assemblyconstructed in accordance with the invention;

FIG.'13 is a schematic diagram of additional structure of the steeringcontrol assembly;

FIG. 14 is a schematic diagram of the main frame tilt,

control assembly as constructed in accordance with the invention;

FIG. 15 is a top plan view of the motor-grader assembly includingcontrol sensor support assembly; and

FIG. 16 is a block diagram of control systems interconnections.

DETAILED DESCRIPTION OF THE INVENTION Referring to FIGS. 1 and 2, amotor-grader assembly 10, consists of an A END mobile assembly 12 and anoppositely oriented B END mobile assembly 14 with a frame assembly 16pivotally supported therebetween. The A END and B END mobile assemblies12 and 14 respectively, may be identical units supported on tandem wheelassemblies 18a. and 18b bearing on rubber tired wheels 20a and 2017,respectively. While motorgrader assembly 10 is shown as being supportedon pluralities of tandem arrayed rubber-tired wheels 20a and 20b, itshould be understood that various other forms of ground supportingmobile means such as traction units, single or plural wheel assemblies,etc., may be employed in the mobile ground supporting function.

Each of mobile assemblies 12 and 14 further consists of a chassis 22aand 22b supported atop tandem wheel assemblies 18a and 18b at a centralpoint (to be further described below) and a suitable power source orengine 24a and 24b is supported thereon. Prototype motorgrader units arepresently designed to include 225 horsepower diesel engines of a typewhich is commercially available from the Caterpillar Tractor Co. ofPeoria, Ill. The engines 24a and 24b function with hydraulic pumps andmotors which are utilized for various power purposes about motor-graderassembly as will be further described below. Hood cowls 26a and 26b areaffixed over respective engines 24a and 24b in secure manner relative tochassis 22a and 22b while conventional bumper structure 28a and 28b,exhaust stack 30a and 30b, and air cleaners 32a and 32b are suitablyadapted.

The main frame assembly 16 is pivotally supported on the A END mobileassembly 12 about a point indicated by vertical axis designation 34, andit is supported at its other end by the B END mobile assembly 14 about avertical axis designation 36. The main frame assembly 16 consists of acentral frame 38 having each end extending into a downward extremitythereof. Central frame 38 has a mounting plate 48 securely affixed as bywelding across its upper, horizontal surface and a pair of bearingshafts 50 and 52 are secured therethrough in parallel, transversedisposition to form a plurality of quadrature arrayed support shafts54,56,58, and 60. Support shafts 54 and extend outward in parallel,spaced and horizontal disposition from one side of central frame 38while support shafts 56 and 58 extend in respective oppositedispositions on the other side of central frame 38.

The end 40 of central frame 38 includes a pair of beams 62 and 64 (seeFIG. 2) and the other end 42 is similarly formed by a pair of taperingbeams 66 and 68. The support shafts 54,56,58, and 60 provide supportconnection for the central frame 38 as they are each pivotally affixedto respective arm ends 70,72,74 and 76 for movement about a transverseaxis. The arm ends 70 and 72 form part of a bifurcated frame 78 whilethe arms 74 and 76 form part of an oppositely disposed bifurcated frame80. Each of bifurcated ends 70,72,74 and 76 receives a semi-circularbearing bracket 82,84,86 and 88 in secure affixure for the purpose ofmovably seizing each of the respective support shafts 54,56,58 and 60.

The opposite or outer ends of the respective bifurcated frames 78 and 80are each mounted to respective mobile assemblies 14 and 12 for pivotalafflxure about vertical axes 36 and 34. The hydraulic cylinder isconnected within bifurcated frame 78 to extend a piston arm 92 intopivotal connection with pivot eye 46 of central frame end 42. Similarly,the hydraulic cylinder 94 is affixed upwardly within bifurcated frame 80to extend a piston rod end 96 downward into pivotal connection withpivot eye 44. Actuation of hydraulic cylinders 90 or 94 enable movementof the central frame 38 relative to each of the bifurcated frames 78 and80 which motion must necessarily extend through to effect counterbalanceat respective tandem assemblies 18b and 18a.

The mounting plate 48 of central frame 38 actually provides a smoothplate about which operating cab 100 is supported. The operating cab 100consisting of operators space 102 and having windshield area 104 issupported on one end of a support arm 106 which, in turn, has it otherend pivotally affixed on mounting plate 48 for movement about a verticalaxis 108. The support arm 106 includes drive and braking mechanism, aswill be further described below, which operates in conjunction withmounting plate 48 to position the operators cab 100 in any desiredposition relative to main frame 16.

A subframe 110, exemplarily shown as being octagonal in construction, issupported beneath main frame 16 in laterally pivotal manner. Thus,subframe 110 is pivotally affixed at a first pivot assembly 12 which isrigidly secured beneath a cross member 114 extending between frame arms62 and 64. Similarly, the opposite end of subframe 110 is pivotallyaffixed to a pivot assembly 116 which is secured beneath a cross member(not shown), secured as by welding between the opposite bifurcated framearms 66 and 68. Pivotal or attitude control of subframe 110 relative tomain frame 16 is exercised by control of a pair of hydraulic cylinders 118 and 120, each of which is pivotally affixed to opposite sides ofcentral frame 38 to extend respective pistons 122 and 124 into asuitable pivotal connection at the opposite sides of the subframe 110. Apair of sensor support arms 119 and 121 extending respective telescopingrods 123 and 125 are securely affixed across opposite sides of subframe110 to extend transversely relative to motor-grader assembly 10.

The subframe 110 provides further movable support of a rotatable ringmember 126 which supports a working implement, an auger-moldboardassembly 128, therebeneath. Ring member 126 is supported for circularmovement within a plurality of support blocks 130 beneath subframe 110,and suitable drive means (as will be further described) are mounted onsubframel10 to provide circular rotation of ring member 126. The workingelement, auger-moldboard assembly 128, is secured beneath ring member126 to rotate therewith. Thus auger-moldboard assembly 128 may consistof an auger element 132a and a blade element 132]: each supported by arespective connecting frame 134a and 134b adjustably connected beneaththe ring member 126. Each of auger and blade elements 132a and 132k areseparately movable as to angle of attack by means of respectivehydraulic cylinders 136a and 136b, such structure to be furtherdescribed in greater detail.

FIG. 3, 4 and 5 depict elements of the B END mobile assembly 14 ingreater detail. It should be understood that the A END mobile assembly12 may be constructed in identical manner. The tandem assembly 18b isactually a commercially available mechanical unit which enables fourwheel drive of tandem arranged wheels, e.g. a separate type final driveutilizing a tandem axle. Casings 140 and 142 of tandem assembly 18b eachinclude a separate sprocket and chain drive for each of the respectivefront and rear wheels 20b. The tandem assemblies include a transverseaxle 144, and a pair of oppositely disposed clamping brackets 145 arewelded beneath chassis 22b to provide secure engagement for support upontransverse axle 144. The tandem axle 144 receives drive rotation from astraight-through gear drive assembly 146 which is connected to receiverotational input through a coupling 148. The rotational input coupling148 is taken from the output of a suitable hydraulic motor 150, e.g. aSeries 27 Sundstrand hydraulic motor as driven from a suitable hydraulicpump 152, e.g. a Series 25 Sundstrand hydraulic pump. While specifichydraulic pump and motor equipment is identified, it should beunderstood that a great many combinations of differing power and typemight be utilized to provide the drive power.

Hydraulic pressure generated in hydraulic pump 152 is also utilized inconventional manner to drive various of the hydraulic control elementdisposed about the motor-grader assembly 10, as will be furtherdescribed. The hydraulic pump 152 is energized from diesel engine 24b asrotational engine output applied to a parallel array of flywheels 154 istransmitted on a plurality of V-belts 156 to a plural belt pulley 158which, in turn, applies rotational input to hydraulic pump 152.Hydraulic pump 152 working in concert with conventional reservoir means(not shown) provides pressure output from a coupling 160 for conductionto an input coupling 162 for energization of the hydraulic motor 150. Anadditional plurality of flywheel pulleys 164 may be used to provide anadditional rotational output from engine 2% for connection to otherauxiliary pump means (not shown) which might be employed for poweringauxiliary implement control mechanisms and such, as will be furtherdescribed below. 7

A vertical pivot shaft 166 is rigidly secured through a floor plate 168of chassis 22b (see also FIG. 6), and into rigid connection on top ofgear box 146 such that is extends vertically from the center of tandemassembly 18b, i.e. straight-up from the intersection of drive axle 144through gear drive 146. Pivot shaft 166 is inserted upward through apivot bearing 170 which is formed to have oppositely disposed yoke arms172 and 174 extending outward for steering connection as will bedescribed. The pivot bearing 170 is also formed to have two oppositelydisposed connecting tabs 176 and 178 (FIG. 5) and these serve to providea connection for tilt control hydraulics as will be described below.

The pivot bearing 170 is mounted on pivot shaft 166 by means of a timkenbearing 180 (FIG. 6) of conventional type interposed concentricallytherebetween to provide necessary ease of the relative movement. Thepivot bearing 170 is formed to have a flange 182 about its upper end,and a frame support bearing 184 having a bottom flange 186 is securelyaffixed thereon, the placement of support bearing 184 also serving toposition and retain the timken bearing 180.

The support bearing 184 provides a rotational support for the frame end78. A steel support rod 188 of suitable size and strangth is securelyaffixed as by welding through the front plate 190 of end frame 78, andsuitable reinforcing such as lateral plate 192 is also provided. Variousheavy construction techniques may be utilized to assure a strong bondbetween rod 188 and fame end 78 since the outer end of rod 188 mustsupport the entire end of the main frame 16 upon mobile assembly 14. Theouter end of rod 188 is rotationally retained within support bearing 84in similar manner as that utilized for pivot shaft 166 within pivotbearing 170 That is, a timken bearing 194 is interposed within theannular space between support rod 188 and the inner surface of supportbearing 184 and a retaining plate 196 is secured over the end of supportbearing 184 in such manner as to assure secure positioning of timkenbearing 194.

Steering control is effected by means of hydraulic cylinders 198 and 200which are connected at pivot ends 202 and 284 to a connecting frame 206which is rigidly secured through transverse beam 288 to the chassis 22b.Hydraulic pistons 218 and 212 are connected to respective yoke arms 172and 174 of pivot bearing 178, and energization in concert of hydrauliccylinders 198 and 200 will provide rotation of yoke arms 172 and 174(pivot bearing 178) relative to the pivot shaft 166 which is alsosecured to chassis 22b of mobile assembly 14.

Tilt control of main frame 16 is effected by control of hydrauliccylinders 214 and 216. Hydraulic cylinders 214 and 216 are eachpivotally mounted by means of respective pivot pins 218 and 220 whichare affixed thereto and pivotally interconnected with bracket plates 222and 224 which are secured through suitable spacers 226 on front plate190 of the bifurcated frame end 78. Hydraulic cylinders 214 and 216extend respective pistons 228 and 230 downward into pivotal connectionwith connecting tabs 176 and 178 as disposed on opposite sides of pivotbearing 170. Coordinated control of hydraulic cylinders 214 and 216effects tilting of frame end 78 and, therefore, main frame 16 about thelongitudinal axis established by the bearing of support rod 188 withinsupport bearing 184.

Frame locking is provided by a hydraulic cylinder 1 232 which may beselectively actuated to extend its piston rod (not specifically shown)into a locking hole which is formed within a locking block 234. Lookingblock 234 consists merely of a block of steel with a hole therethroughand which is secured at a front center point of forward plate 190 of endframe 78. Hydraulic cylinder 232 is then supported in longitudinalrelationship by a mounting plate 236 suspended by a pair of supportplates 238 each rigidly secured above the support bearing 184. Theoperator can effect control of cylinder 232 to extend the piston intolocking block 234, this serving to maintain continuous positioning ofthe hydraulic locking cylinder 232 in vertical alignment, said verticalalignment assuring lateral horizontal positioning of frame end 78.

Referring now to FIG. 7, the main frame 16 is provided with uniqueadjustability through pivotal connection of end frames 78 and to thecentral frame 38. The subframe is secured from pivot assemblies 112 and116 from opposite ends of central frame 38. That is, a bearing sleeve240 secured from a sleeve hanger 242 as rigidly affixed beneathtransverse member 114 (FIG. 2), a part of the main frame 38, is securedabout the bearing pin 244 as supported by plates 246 and 248. Pivotassembly 116 at the opposite end is similarly constructed and supportedfrom the opposite end of main frame 38 with a hanger 250 supporting abearing sleeve 252 for pivotal support about a bearing pin 254 assecured between vertical plates 256 and 258.

A plurality of adjustable ring support blocks (FIG.2) are disposed atapproximately equal distances about the underside of subframe 118 tosupport the ring member 126 moveably therearound. Each of support blocks130 is individually adjustable for initial setting of level andcentering of the ring 126. A ring drive hydraulic motor 260 is suitablymounted to work into a worm gear 262 which transmits rotational force toa 126. Referring to FIG. 7, each of the implement extending panels 134aand 13411 which serve to pivotally support adjusting plates 272a and272b about pivotal connections 274a and 274b. The blade element 132b issecured by a suitable form of rigid connection 276b to said adjustingplate 272b for movement therewith. Hydraulic cylinder 136b, pivotallyconnected to ring member 126, extends a piston 278b into pivotalconnection with a lever mechanism 280b which exerts positioning controlon the blade element 132b. The bydraulic adjusting cylinder 136b, aswell as adjusting plate 272b, connecting mechanism 276b and otherrelated components are duplicated on each side of the ring member 126,ie as associated with each of opposite-side implement support panels270. The auger element 1320 is secured in like manner by means of asuitable form of connection 276a as secured to a transverse frame member271 and adjusting plate 272a for movement therewith. The hydrauliccylinders 136a (one on each side of ring member 126) extend respectivepistons 278a into pivotal connection with lever mechanisms 280a forpositioning control.

Referring now to FIG. 8, the auger element 132a may consist of anelongated cylinder 282 having a vane 284 arranged therearound in helicalflight, the vane 284 being secured as by welding in helicalconfiguration. The ends of cylinder 284 are then connected via shafts286 and 288 for rotational retention within oppositelydisposed supportassemblies 290 and 292 which extend from transverse frame member 271. Ahydraulic motor 294 of well-known type is affixed to the outer portionof support member 292 to impart rotational drive to shaft 288. Ifdesired, additional hydraulic drive can be imparted from a hydraulicmotor 296 providing input to the opposite shaft 286. The hydraulicmotors may be selected of desired rating from any of variouscommercially available types. In addition, although not specificallyshown herein, it is contemplated that the auger element 132a may bebroken in the middle, each half being separately, rotationally supportedby suitable framing at the mid-point, so that each of the two sides maybe independently-driven at the same or different rotational speeds.

FIG. 9 illustrates an alternativeform of auger element 298 of thecutter-auger type which includes a first helical flight of cutter bars300 each carrying a cutter head 302 and a second helically arranged vaneflight 304 wound in intersticed relationship. The cutter-auger 298enables a rotary cutting action which has greater trimming and clearingcapabilities, and which is especially attractive for use uponencountering certain difficult or highly compacted forms of earthmaterial. The cutter-auger 298 may be disposed for use withhydraulically drive and support elements similar to those as shown inFIG.8.

In prototype equipment, the various control power functions about themotor-grader assembly have been effected by the use of hydraulicequipment; however, it should be understood that these functions can beperformed by any of the conventional powering methods such aselectrical, pneumatic, mechanical, or any combination of such powercircuits. Control functions are readily regulated by the operator in themovable operating cab and, in addition to manual control, it is oftendesirable to enable automatic control of certain level and steeringfunctions so that the motor-grader assembly 10 can be controlled totallyor in part from an external grade reference such as a string line. Suchmanual-automatic control functions as specifically directed to hydraulicequipmentation are more particularly set forth hereinafter.

As shown in FIG. 10, a frame level control 312 provides setting of theelevation and level of main frame assembly 16. Such height control iseffected by adjustment of the hydraulic cylinders and/or 94 (see alsoFIG. 1). A dual control assembly 314, situated in the operators cab 100,provides a first manual lever switch 316 for controlling A END elevationand a second manual lever control 318 for controlling B END height.

A pair of hydraulic connections 318 and 320 are connected to hydrauliccylinder 94 and to a four-way valve 322. The hydraulic valve 322 is acommercially available four-way type which has a quiescent or lockcentral portion 324 as well as oppositely porting spool sections 326 and328. The valve 322 is then controlled by energization of one or theother of the end-mounted solenoids 330 and 332 which provide the properflow of hydraulic fluid to the hydraulic cylinder 324. Hydraulicconnections 334 and 336 are shown connected to a sump which may be anysuitable form of hydraulic pump and reservoir system compatible with theavailable power requirements and drive input energy.

Manual lever switch 316 provides A END control by energization ofelectrical leads 338 and 340 to actuate one or the other of solenoids330 and 332. Similarly, manual lever 318 provides B END actuation byenergization of respective ones of electrical connections 342 and 344 toactuate solenoids 346 and 348. These solenoids 348 and 346 provideopposite actuation of a fourway hydraulic valve 350 which has a centrallock up section 352 as well as oppositely flowing port sections 354 and356. l-Iydraulic lines 358 and 360 connect between hydraulic cylinder 90and four-way valve 350, with hydraulic lines 362 and 364 leading to asuitable hydraulic pressure sump.

The schematic representation of FIG. 11 illustrates a control system 366which controls the cross slope of the subframe l 10 and whatever theworking implement suspended therebeneath. The subframe has its crossslope adjusted in accordance with the actuation of hydraulic cylinders118 and 120 which are oppositely connected in parallel to hydrauliclines 368 and 370 from a four-way valve 372 thereby to effect reciprocalcylinder action. Four-way valve 372 is connected to source hydrauliclines 374 and 376, and valve 372 consists of a lock up section 378 aswell as opposite porting sections 380 and 382 which are positioned byoppositely actuating solenoids 384 and 386, respectively.

Solenoids 384 and 386 are controlled via electrical connections 388 and390 from a suitable cross slope selector 392 which in turn, receivesinput from a manual cross slope control 394 and an automatic cross slopecontrol 396. The manual cross slope control 394 may be located in theoperating cab 100, while the automatic cross slope control 396 refers tocontrol energization originating from suitable control sensors which areresponsive to an external reference, as will be further described below.The automatic cross slope control 396 may be such as a gravityresponsive switch with suitable output which is adjustable in relationto a pendulum or such.

Referring now to FIG. 12, an automatic-manual steering system 400includes A END steering assembly 402 and a B END steering assembly 404.Manual steering is carried out by means of a steering control unit 406,the subject matter of FIG. 1 1 as will be further described, withsteering end selection being made through a manual steering end selectorswitch 408. Automatic steering in response to sensing of an externalreference is carried out in response to an A END steering control 410 ora B END steering control 412 as se lected by a steering selector 414 forinput via leads 416 and 418 to each of an A END four-way valve 418 and aB END four-way valve 420.

Manual steering is carried out by steering control unit 406 which iscontrolled to steer one end or the other in response to actuation ofmanual steering end selector 408. Thus, in the case where the A ENDassembly 402 is to be steered, hydraulic fluid output in one directionor the other is present on hydraulic lines 422 and 424 to a double-endedhydraulic cylinder 426. The hydraulic cylinder 426 has one end 428pivotally connected to a valve spool 430 of a heavy duty hydraulic valve432, e.g. a thirty gallon four-way valve. The hydraulic valve 432 isenergized by hydraulic pressure present on hydraulic lines 434 and 436from a suitable sump, and valve output is directed through hydrauliclines 438 and 440 which are applied in opposite, parallel connectionthrough respective steering cylinders 198a and 200a. Thus, applicationsof pressure differential, as between hydraulic lines 438 and 440,results in reciprocal action ofhydraulic cylinder pistons 212a and 2100to effect pivoting of the steering yoke 172a-l74a which is in rigidaffixure to the main frame 16.

Steering of the B END steering assembly 404 is effected by applicationof a hydraulic fluid differential between hydraulic lines 442 and 444 toa double-ended hydraulic cylinder 446. The hydraulic cylinder 446 drivesa reciprocal valve spool 448 of a heavy duty hydraulicvalve 450 in thesame manner as described for the A END assembly. That is, hydraulicsource input is via lines 452 and 454 with regulating fluid output alonghydraulic lines 456 and 458 to each of the hydraulic steering cylinders460 and 462. The fluid input to hydraulic cylinders 460 and 462 is inparallel but opposite orientation to effect reciprocal movement ofrespective piston rods 210 and 212 thereby to effect steering movement.

Automatic steering,- as might be effected from suitable control sensorsoperating in response to an external reference, would originate as anelectrical control signal in the form of a switch closure via leads 416through 419 to energize predetermined valve solenoids. Thus, anenergizing voltage on lead 416 to valve solenoid 418 changes four-wayvalve 418 from its center or lockup position 470 to spool position 472which directs hydraulic fluid from pressure source lines 474 and 476through respective hydraulic lines 438 and 440 to cause reciprocalenergization of hydraulic cylinders 198a and 200a. Energization via lead417 energizes solenoid valve 478 such that valve spool section 480effects an opposite hydraulic pressure differential as between.hydraulic lines 438 and 440. Upon deis effected in similar manner. Thatis, electrical energization of 'either of leads 418 or 419 actuatesrespective valve solenoids 483 and 484. Actuation of solenoid valve 482moves the valve spool from its lockup position 486 to the position wherespool section 488 directs hydraulic fluid flow from source lines 490 and492 through respective supply lines 456 and 458. Alternate energizationof the valve solenoid 484 places spool section 494 in operation toreverse the pressure differential as between hydraulic lines 456 and458, this effecting an opposite reciprocal effect as between thesteering cylinders 460 and462.

The steering control unit 406 is shown in greater detail in FIG. 13which includes various valve interconnections for responding to themanually operated steering wheel 500. Steering wheel 500 is connected bymeans of a suitable mechanical linkage 502 to operate an orbitrolmechanism 504. The orbitrol 504 is a wellknown type of hydraulicproportioning pump which varies the direction and force of hydraulicflow as between pressure lines 506 and 508. The lines 506 and 508 areconnected to supply fluid pressure input to respective four-wayhydraulic valves 510 and 512 with pressure return proceeding viahydraulic lines 514 and 516 to a fluid reservoir 518. Pressure relief isafforded by a common fluid connection 520 through oppositely orientedcheck valves 522 and 524 with return to the respective input pressurelines 506 and 508.

Electrical input from manual steering end selector 508 (FIG. 12) isprovided by signal input on leads 526 and 528. Thus, input on lead 526energizes solenoid valves 530 and 532 to bring respective valve spoolsections 534 and 536 into function, this enabling A END steering controlof the A END cylinder 426. Energization on lead 528 actuates valvesolenoids 538 and 540 to move spool sections 542 and 544 in the properflow position such that the B END cylinder 446 is energiz-- ableinresponse to the adjustment of orbitrol 504 for manually steering themotor-grader assembly. The center spool positions 546 and 548 of therespective fourway valves 510 and 512 merely provide pressure balancingporting.

Referring now to FIG. 14, a main frame tilt control assembly 550exercises selected control of lateral tilting of the A END or the B ENDor both ends simultaneously of the main frame relative to the respectiveA END and B END mobile assemblies 12 and 14. As shown, the B END is inthe unlocked position as B END unlock control 552 provides energizingvoltage via lead 554 to energize valve solenoid 556 such that a four-wayvalve 558 is actuated to energize hydraulic locking cylinder 232 suchthat its locking piston 560 is withdrawn out of engagement with lockingblock 354. Alternately, the A END unlock 562 will be de-energized suchthat valve solenoid 564 does not actuate a four-way valve 566. In thisposition, the valve 566 actuates locking cylinder 3630 such that alocking pin 560a is forced into locking engagement within locking block234a.

When the A END unlock 562 de-energ izes to cause locking of the frame AEND, a B END tilt control 568 may then be controlled by energizationalong either of electrical ends 570 or 572 to effect frame tiltingrelative to the B END mobile assembly. Energization of lead 570energizes valve solenoid 574 such that a fourway valve 576 is actuatedfrom its lockup spool section 578 to a spool section 58010 place apressure differential between hydraulic lines 582 and 584.

When the A END unlock 562 is energized to withdraw the locking pin 560athe hydraulic tilt cylinders 216a and 214a may be energized to effectlateral tilting of main frame. Thus, an A END tilt control 590 may beselectively actuated to energize one or the other of leads 592 or 594 toenergize respective solenoids 596 or 598. A hydraulic valve 600 isnormally positioned with the lockup spool section 602 in circuit withpressure lines 604 and 606 and the hydraulic circuit lines 608 and 610.Pressure lines 608 and 610 are then connected in parallel to each of thehydraulic tilt cylinders 216a and 214a to effect reciprocal pistonaction upon energization of either of relays 596 or 598. Energization ofrelay 596 brings valve spool section 612 into function, whileenergization of relay 598 will bring the opposite valve spool section614 to cause reverse pressure application.

A hydraulic override function is provided at each frame end throughoperation of check valves 616, 618, 620 and 622. Thus, not until the BEND is unlocked with energization of valve solenoid 556 can thehydraulic tilt cylinders 216 and 214 be actuated. In the unlockattitude, valve spool section 558 applies pressure via hydraulic line624 to open each of the respective check valves 616 and 618 such thatthey will then allow hydraulic pressure application as present on eitherof hydraulic lines 582 and 584 to the tilt control cylinders 214 and216. Similarly, check valves 620 and 622 are open with application ofpressure on hydraulic line 626 (opposite from that shown) to allowhydraulic actuation of tilt cylinders 214a and 216a.

Referring now to FIG. 15, a motor-grader assembly carries a suitabletracer bar 630 suspended in outrigged position as carried by supportarms 119 and 121 and respective telescoping rods 123 and 125. Supportarms 119 and 121 are each welded to opposite segments of subframe 110 toextend laterally outboard, while telescoping rods 123 and 125 areadjustably held within support frames 119 and 121. Telescoping rods 123and 126 may be extended outward to any length as desired. A pair ofpivotal brackets 632 and 634 serve to secure the sensor rods 630 on theends of respective telescoping rods 123 and 125. The brackets 632 and634 should be a suitable pivot assembly since it will quite often berequired that telescoping rods 123 and 125 extend outward differentdistances. Such will be the case when motor-grader assembly 10 isoperated along an external reference or string line 636 with main frame16 canted relative to the A END and B END mobile assemblies 12 and 14.It should also be understood that telescoping rods can be readily fittedto extend outboard in the other direction, from the opposite ends ofsupport arms 119 and 120, as exigencies demand.

A bracket 638 and support 640 aid in the automatic steering function bycarrying a control sensor box 642 having a sensor rod 644 which isguided relative to string line 636. Automatic steering function at theopposite end is carried out by bracket 646, support arm 648, control box650 and sensor rod 652. The length- ,wise placement of control sensorboxes 642 and 650 may also-be carried for differing applications. Thus,sensor boxes 642 and 650 may be aligned with the leading and trailingedges of the furthest displaced (lengthwise) wheels of respective mobileassemblies 12 and 14 as is shown in FIG. 15.

Automatic elevation sensing indications are also derived from stringline 636 by means of brackets 654 and 656 which support additionalcontrol assemblies. Bracket 654 supports a control sensor box 656 and acounter-weighted sensing rod 658 which travels along string line 636.Similarly, bracket 656 carries a control sensor box 662 having aweighted sensor rod 664. The control sensor boxes 642, 650, 658 and 662may all be a similar type such as is disclosed in a U.S. Pat. No.3,514,630 entitled Line Tracer Control Device and issued in the name ofSteele et al. Such control sensor box provides an electrical output inresponse to sensing variations relative to string line 636, suchelectrical signals being conducted back to appropriate controlassemblies on the structure of motor-grader assembly 12.

The block diagram of FIG. 16 illustrates the interconnection of thevarious sensing and control components. Thus, output from A END steeringsensor 650 is applied to steering selector 414 which may be a main panelcontrol located in the operating cab 100. In the automatic attitude, AEND steering output from line 670 is applied via line 672 to causeproper function of hydraulic valve 418 such that steering cylinders 198aand 200a are driven to effect a steering correction of the A END mobileassembly 12. Similarly, output from B END steering sensor 642 isconducted via lines 674 through steering selector 414 to a control lead676 which actuates hydraulic valve 420 to effect steering actuation ofthe B END steering cylinder 198 and 200. Manual steering control frommanual control unit 406 is an override control controlling selected onesof hydraulic valves 432 and/or 450 as shown more clearly in FIGS. 12 and13.

Automatic elevation sensing takes place in similar manner in response tosensor control boxes,i.e. A END elevation sensor 662 and B END elevationsensor 658. The respective outputs are applied via leads 678 and 680 forcircuit selection in selector 329. Selected outputs via control leads682 and 684 are applied to respective hydraulic valves 322 and/or 350 toeffect variation of height control cylinders 94 and 90.

It is also contemplated that cross slope control be carried outautomatically by a suitable form of transversely oriented sensor whichprovides zero or no output indication relative to a preset elevationvalue. Thus, a suitable transverse level sensing mechanism may provide acontrol output for use in either the cross slope circuitry (FIG. 11) orthe main frame tilt control circuitry and hydraulics (FIG. 14) or both.Such control output could be applied to effect automatic following ofsupport structure which holds auger 132a and moldboard 1321: at propercutting angle.

Operation The motor-grader assembly 10 is capable of operation in eitherlongitudinal direction under control of either an operator or anassociated external reference such as a string line. FIGS. 15 and 16illustrate the manner whereby automatic elevation and steering sensingare carried out with reference to string line 636. In this case, thesensor positions are adjacent opposite longitudinal extremities of themotor-grader assembly 10 and in parallel disposition to main frame 16.It should be understood however that sensor rod 630 can be aligned atany angular relationship relative to main frame 16, depending upon theangle of attach of the motor-grader assembly in performing itsearth-working undertaking.

Referring also to FIG. 12, automatic steering is carried out in responseto A END steering control 410 and B END steering control 412 operatingthrough steering selector 414. That is, more particularly, electricaloutputs from A END steering sensor 650 and B END steering sensor 642(FIG. 16) as applied for selective actuation of hydraulic valves 418 and420. Thus, for A END steering, a sensed electrical output from A ENDautomatic steering control 410 is conducted via one or the other leads416 and 417, depending upon the direction of turning, to activate theassociated valve solenoid 468 or 478 such that hydraulic valve 418provides the requisite pressure direction through steering cylinders198a and 200a.

Manual steering is effected in a different manner utilizing overridingpower application with the orbitrol and steering wheel structure of FIG.13. In this case, steering wheel 500 is manipulated to vary the orbitrolpump 504 to operate the proper one of A END or B END hydraulic valves510 or 512. The valves 510 and 512, in turn, serve to energizerespective drive cylinders 426 and 446 to position the hydraulic valvespools within respective hydraulic cylinders 432 and 450 (FIG. 12).Valves 432 and 450 are heavy duty hydraulicvalves which allow manualsteering as an override function with continual correction being appliedfrom an automatic steeringsource which may actuate then conducted vialeads 682 and 684 to energize one or both of hydraulic valves 322 and350 to activate their respective height control cylinders 94 and 90located at each end of the main frame 16. Selector 329 also allows useof manual adjustment control 314 which provides parallel control ofhydraulic valves 322 and 351).

The auger-moldboard assembly 128 is maintained in proper workingattitude to a selected earth plane through control of the ring member126. Thus, control of central frame 38, by actuation of hydrauliccylinders 90 and 94, allows setting at any selected longitudinal angle;and hydraulic cylinders 118 and 120 are controlled to set the transverseangle of the ring member 126 with respect to the central frame 38 and,therefore, at desired angle to the earths surface therebeneath. It isalso contemplated to employ cross slope sensing to provide continualautomatic-control of the transverse attitude of the auger-moldboardassembly 128.

It should be understood that various other schemes, both automatic andmanual, may be employed in controlling a motor-grader constructed inaccordance with the invention. Automatic control measures may includevarious other external references in addition to the conventional stringline practices, such references being delineated by such as lighteffects, relative gravity effects, surface or slab sensing, etc. Also,while the motor-grader assembly is shown as carrying a cutter-augerimplement 128, it is contemplated that still additional attachmentaccessories such as ripping implements, trimmer-spreader attachments,excavator assemblies, scanifiers, etc. may be carried beneath the mainframe in operative alignment to carry out the earth-working function inresponse to either manual or automatic control.

The foregoing discloses a novel-working combination for accessoryutilization with motor-grader assemblies, such machines serving toenable greater work efficiency per time expenditure. A double-endedmotorgrader assembly has the additional advantage of being reversible inoperation such that various turning around maneuvers are eliminated, andthis serves to cut down greatly on job time. The control systemsdisclosed herein offer particular advantages in steering and elevationcontrol of such double-ended machines, elevation control being effectedsuch that an entire midframe assembly is variable both as to elevationand level relative to the earth or other selected references, andautomatic-manual steering can be effected even from an offset or cantedmidframe position, as may be required in particular earth-workingsituations. The further combination of the rotary cutter and moldboardwork implements, functioning in coaction, enable operational advantagesheretofore unrealizable in motor-grader apparatus or, for that matter,any single type of mobile machine of relatively general earthworkingapplication.

Changes may be made in combination and arrangement of elements asheretofore set forth in the specification and shown in the drawings; itbeing understood that changes may be made in the embodiments disclosedwithout departing from the spirit and scope of the invention as definedin the following claims.

What is claimed is:

l. Earth-working apparatus comprising:

first and second mobile means each including drive power source andmobile structure;

central frame means of generally elongated form having each of first andsecond ends pivotally affixed to respective first and second mobilemeans for support therebetween;

subframe means secured to and pivotally supported from said centralframe means;

ring member means rotatably affixed beneath said subframe means forcircular rotation thereof;

rotatable auger means rotatably and pivotally affixed beneath said ringmembers for circular rotation therewith;

moldboard means disposed generally parallel to said auger means andpivotally affixed beneath said ring member means for circular rotationtherewith; first and second control means for adjusting the position ofeach of said augermeans and mold-board means relative to said ringmember means; and means accomodating an operator rotatably affixed ontop of said central frame means for selected positioning thereon to gainoptimum surveillance.

2. Earth-working apparatus as set forth in claim 1 wherein said firstand second control means comprise:

first and second hydraulic cylinder means each pivotally connectedbetween said ring member and the respective auger means and moldboardmeans.

3. Earth-working apparatus as set forth in claim 1 which is furthercharacterized to include:

drive means connected to said auger means to impart rotationable driveforce to said auger means.

4. Earth-working apparatus as set forth in claim 3 wherein said drivemeans consists of a hydraulic motor.

5. Earth-working apparatus as set forth in claim l which is furthercharacterized in that:

at least a portion of said central frame means is adjustable as to thelongitudinal angle; and

means for adjusting said longitudinal angle of said central frame meansportion.

6. Earth-working apparatus as set forth in claim 1 which is furthercharacterized in that:

at least a portion of said central frame means is adjustable as tolongitudinal angle; and

means for adjusting said longitudinal angle of said central frame meansportion.

7. Earth-working apparatus as set forth in claim 1 wherein said augermeans comprises:

central shaft means of generally elongated form; and

vane means arranged in a continual helical flight making a plurality ofrevolutions around said shaft means along the length thereof.

8. Earth-working apparatus as set forth in claim 7 which is furthercharacterized to include:

a plurality of toothed cutter elements arranged in a helical flight andextending around said central shaft means a plurality of times at apre-set distance displaced from said flight of vane means.

9. Mobile earth-working apparatus, comprising:

frame means;

subframe means pivotally supported from the frame means;

ring member means rotatably affixed beneath the subframe means forcircular rotation thereof;

rotatable auger means rotatably affixed beneath the ring member meansfor circular rotation therewith;

moldboard means disposed generally parallel to the auger means andaffixed beneath the ring member means for circular rotation therewith;

hydraulic cylinder means secured to the frame means and to the subframemeans pivotally controlling the attitude of the subframe means; therebycontrolling the attitude of the auger means and the moldboard means; andcontrol means connected to the auger means and the moldboard meansadjusting each relative to the subframe means, the control meanscomprising: first and second hydraulic cylinder means each having oneend connected to the subframe means and having respective remaining endsconnected to the moldboard means and the auger means; and actuationmeans for controlling the hydraulic cylinders to raise and lower themoldboard means and the auger means. 10. Apparatus as set forth in claim9 wherein said auger means comprises:

central shaft means of generally elongated form; vane means arranged ina continual helical flight and extending a plurality of revolutionsaround said shaft means along the length thereof. 11. An apparatus asset forth in claim 10 which is further characterized to include:

a plurality of toothed cutter elements arranged in a helical flightextending around said shaft means a plurality of times at a pre-setdistance displaced from said flight of vane means.

1. Earth-working apparatus comprising: first and second mobile meanseach including drive power source and mobile structure; central framemeans of generally elongated form having each of first and second endspivotally affixed to respective first and second mobile means forsupport therebetween; subframe means secured to and pivotally supportedfrom said central frame means; ring member means rotatably affixedbeneath said subframe means for circular rotation thereof; rotatableauger means rotatably and pivotally affixed beneath said ring membersfor circular rotation therewith; moldboard means disposed generallyparallel to said auger means and pivotally affixed beneath said ringmember means for circular rotation therewith; first and second controlmeans for adjusting the position of each of said auger means andmold-board means relative to said ring member means; and meansaccomodating an operator rotatably affixed on top of said central framemeans for selected positioning thereon to gain optimum surveillance. 2.Earth-working apparatus as set forth in claim 1 wherein said first andsecond control means comprise: first and second hydraulic cylinder meanseach pivotally connected between said ring member and the respectiveauger means and moldboard means.
 3. Earth-working apparatus as set forthin claim 1 which is further characterized to include: drive meansconnected to said auger means to impart rotationable drive force to saidauger means.
 4. Earth-working apparatus as set forth in claim 3 whereinsaid drive means consists of a hydraulic motor.
 5. Earth-workingapparatus as set forth in claim 1 which is further characterized inthat: at least a portion of said central frame means is adjustable as tothe longitudinal angle; and means for adjusting said longitudinal angleof said central frame means portion.
 6. Earth-working apparatus as setforth in claim 1 which is further characterized in that: at least aportion of said central frame means is adjustable as to longitudinalangle; and means for adjusting said longitudinal angle of said centralframe means portion.
 7. Earth-working apparatus as set forth in claim 1wherein said auger means comprises: central shaft means of generallyelongated form; and vane means arranged in a continual helical flightmaking a plurality of revolutions around said shaft means along thelength thereof.
 8. Earth-working apparatus as set forth in claim 7 whichis further characterized to include: a plurality of toothed cutterelements arranged in a helical flight and extending around said centralshaft means a plurality of times at a pre-set distance displaced fromsaid flight of vane means.
 9. Mobile earth-working apparatus,comprising: frame means; subframe means pivotally supported from theframe means; ring member means rotatably affixed beneath the subframemeans for circular rotation thereof; rotatable auger means rotatablyaffixed beneath the ring member means for circular rotation therewith;moldboard means disposed generally parallel to the auger means andaffixed beneath the ring member means for circular rotation therewith;hydraulic cylinder means secured to the frame means and to the subframemeans pivotally controlling the attitude of the subframe means; therebycontrolling the attitude of the auger means and the moldboard means; andcontrol means connected to the auger means and the moldboard meansadjusting each relative to the subframe means, the control meanscomprising: first and second hydraulic cylinder means each having oneend connected to the subframe means and having respective remaining endsconnected to the moldboard means and the auger means; and actuationmeans for controlling the hydraulic cylinders to raise and lower themoldboard means and the auger means.
 10. Apparatus as set forth in claim9 wherein said auger meaNs comprises: central shaft means of generallyelongated form; vane means arranged in a continual helical flight andextending a plurality of revolutions around said shaft means along thelength thereof.
 11. An apparatus as set forth in claim 10 which isfurther characterized to include: a plurality of toothed cutter elementsarranged in a helical flight extending around said shaft means aplurality of times at a pre-set distance displaced from said flight ofvane means.